Weighing and indicating mechanism



March 15, 1938. F. Q. RAST 2,111,127

' I WEIGHING AND INDICATING MECHANISM 4 Sheets-Sheet 1 Filed May- 7,1935 Ill-"n E llillll Will-HIM Ill-"Iii ATTORN EY March 15, 1938.

Filed May 7, 1935 4 sheets-sheet 2 7 sso .5 5 TEE ee 7 7y 38 r I 4 I L127 a0 f; r;

a V o if N%\95' 72 777' INVENTO ATTORNEY March 15, 1938. E RA T2,111,127

WEIGHING AND INDICATING MECHANISM Filed May 7, 1935 4 SheetsSheet 5ATTORNEY March 15, 1938. E RAST 2,111,127

' WEIGHING AND INDICATI NG MECHANISM Filed May 7, 1935 4 Sheets-Sheet 4F IG.4. 43

ATTORNEY Patented Mar. 1938 UNITED STATE HANISM Frederick Q. Rast,Binghamton, N. Y.. assignor to International Business MachinesCorporation, New York, N. Y., a'corporation of New 'York Application 1iClaims.

This case relates to a scale with weight recording, indicating,exhibiting, or manifesting means.

The object is to provide simple means to obtain a value manifestation orrecord in a lower order denomination of a load value without directlysetting such means by the load force.

More specifically, the above object is to provide means for obtainingfractional pound readings, preferably in ounces; without direct settingby the load force. I

"Further, the object is to look a load set member and by such looking toset a value manifesting means mounted for movement independently of theload set member.

Still further, the object is to set a load responsive member in an evenload. position and by such action to set a fraction load valuemanifesting means.

The object is also to effect the load setting of a higher order valuemanifesting means while it is free of means to supplement the loadsetting and to then operate the latter means tosecondarily set thehigher order manifesting. means at an integral load position and by sodoing set a lower order or lower orders of value manifesting means.

Other objects will appear. from-the following parts of the descriptionand from the drawings.

Inthe drawings:

Fig. 1 is a vertical end section through one end of the machine, 1

Fig. 2 is a section along line 2-2 of i,

Fig. 3 is an end-section through the machine showing the parts ininitial positions,

.Fig. 4 is a view similar to Fig. 3 but in operated positions, 1

Fig. 5 shows the operating motor and clutch control,

Fig. 6 is the circuit diagram, and

Fig. '7 is the timing diagram;

The weighing means comprises platform to legs ll. of which are supportedby first principle. loase levers l2 andflS. lever I2 is connected thewith parts power end to linkfld, actuating a third lever it. The powerend or" lever i5 is connected by tape it to a sector ll on shaft i8carrying pendulum M May ":1, 1935, Serial No. 20,138

. (Ell. 265-5) chart 26, the rim of which is graduated in pounds andounces, with the pound graduations marked by the corresponding figures.The chart is viewed through sight window fl (Fig. 3) in the front ofcasingiiiand indexed by sight line 29.

For purposes of the disclosure, it will be as sumed the scale has acapacity of (l to making seventy pound divisions. The left side of chart26 (as viewed in Fig. 2) rigidly carries notched disk 30 having seventynotches 3i, one for each pound graduation of chart 26. At the right ofchart 26, its shaft 22. carries a tens order stepped disk 32 and a unitsorder stepped disk Disk 32 has steps 34 of difierent radial heights torepresent tens of pounds values 0, 1, 2-6. Each step ttcovers a range often pound divisions of chart 265. Disk 33 has a series of ten steps 35each series coextensive steps it of disk The steps 3? of a series differin height to represent values 0 to 9 in the units. of pounds order andeach step covers a single pound division of chart it. To indicate thevalue represented by .a step 36 or 35, the digit indicating the valuewill be appended to the common reference character.

Thus with .a load on the scale of lbs., steps- 34-Q and 359-5 will beset in control positions.

Between frames it and 25 is a third frame 36 (Fig. 2) with a ballbearing 3! forthe. left end of a sleeve shaft 38 surrounding but nottouching weight shaft 22. The right end of shaft 38 is journalecl inbearing ill carried by frame 25. Operation of shaft t2 under. a load hasno effect upon shaft 33.

Shaft 38 carries, to the right of disks 32 and it, the t-ensorder ouncedisk 39 and the units order ounce disk it. The outside peripheries ofdisks 39 and it are each at a radius equal to that of a zero step St orand therefore represent zero and rack sector 2d. Sector 20 meshes withpinion A it on weight shaft 22-to rotate the latter clockwise (as viewedin Fig. 1) or counterclockwise (as viewed in Figs. 3 and 4) when a loadis applied to the platform.

As indicated in Fig. 2, shaft 22 extends to the right of platform It andis journalecl at opposite ends in bearings carried by frame plates orstand ards 24 and 25.- Shaft 22 carries cup-shaped values in the tensand units ounce orders. Disk 39 has a single step ii-l representingvalue i in the tens ounce order. Disk W has a series of nine steps ti-i,2, 3,- .9 coextensive with an arc of disk 39 just preceding step tl-i.Following the series of nine steps t2-i to E9, disk iii has a series ofsteps l2@, i, 2, 3,-@ representing values 0 to 6 in the units ounceorder and lying along an arc coextensive with step ii-l of disk Acombination of the disk steps 4i and it represents the ounce value of aload. Thus, step ii-t (the outside periphery of disk t9) and step 69pounds,

with one of the it-8 represent 8 ounces, step ll-i and step levers l2,l3, and I! are rocked to pull down on tape l6 causing gear sector 23 torock cl kwise (Fig. 1) and similarly rock shaft 22 with its chart 26 andstepped disks 32 and 33 according to the load. For example, a load oitwenty-five pounds and eight ounces will bring the corresponding 25 lbs.graduation of chart 26 to sight line 23 and will set a step 34-2 of disk32 and a step 35-5 of the series of steps-of disk 33 coextensive withstep 342 at control position. Under control of these steps, the tens andunits pound order load record will be made, as will be later broughtout. In order to control the recording of the ounce value of the load,which in the above example, is 8 ounces, disks 33 and 43 must be set tobring the steps 4|3 and 4|3 to control position. The means for doingthis will now-be explained.

Referring to Figs. 2, 3, and 4, frame plate 24 has a guide bracket 43 atthe upper end for slidably receiving and guiding the upper portion of acontrol bar 44. The lower portion of bar 44 has a slot 440 'slidablycoacting with a stud 45 on frame 25.

The upper end of bar 44 is pivoted to a lver 46 which is pinned at anintermediate point to the core 41 of a solenoid 43. A spring 43connected to lever 46 normally holds core 41 and control bar 44 at theirupper limits. The portion of bar 44 passing through guide bracket 43 hasa vertical slot 53 receiving pin 5| extending from one side of a slideblock 52 slidably mounted within bracket 43. The lower part of block 52is formed to provide a knife edge tooth 53 which lies along the planeincluding notched disk 30.

The tooth has a side extending radially of disk 30 and a side inclinedto the radial side. Similarly, each notch 3| has a radially directedside and a side inclined thereto. The angle between the sides of a notchis the same same angle between the sides of tooth 53 and the dimensionsoi' the tooth are such that the tooth will fit snugly in a notch 3|. Forconvenience, the radially directed side of a notch or of tooth 53 may bereferred to as the abrupt side while the side inclined to the radiallydirected side may be referred to as the inclined or cam side of a notch3| or'of tooth 53.

As previously stated, there are seventy notches 3| one for each of poundvalues 0 to 69. The

points of the teeth 3| which form notches 3| ment. Now, should tooth asbe moved me at pound distances apart and each point corresponds to aneven-pound graduation of chart 26. Further, these points pass the pointof knife edge 53 in step with the travel of the corresponding poundgraduations past index 23. Since each notch corresponds to a range ofone pound, the notch may be considered as divided into sixteen equaldivisions, each equivalent to an ounce range of chart 26. If the load onthe scale is an even poundage, then the point of a tooth 3| whichcorresponds to such load value will be exactly opposite the point oftooth 53 and the abrupt sides of tooth 53 and the notch to the right oftooth 53 (Fig. 3) will be in radial alinetowards disk 33, the point ofthe tooth and the point of I disk 33 corresponding'to the load mayengage and stop movement of the tooth. The disk 33 will thereby belocked in an even pound position. Should the tooth 53 move oil the evenpound point of disk 30 and into the notch 3| at the right oi this point(as viewed in Fig. 3), then the'abrupt sides of this notch and of tooth53 will merely engage along a radial line and as a result, the toothmovement will not eifect movement oi disk 30 but on the contrary willlock it inits even pound position.

Should the tooth 53 move oil the even pound point and into the notch 3|at the left of this,

point, then the inclined sides of this notch and of tooth 53 will camagainst each other as the tooth moves downwardly and as a result, whenthe tooth has fully and snugly entered this notch, disk 33 will havebeen moved backwards, in a descending load direction, clockwise (asviewed in F18. 3) to the extent of a full notch width. This isequivalent to returning disk 30 through a full pound value and therebysubtracting one pound from its primary load setting. However,

through means presently to be described, the

backward or reverse movement of disk 30 causes corresponding movement ofstepped ounce disks 33 and so that if the disk 33 has been reversed afull pound, disks 33 and 43 will be set to read out a value of 16ounces. Thus, for an even pound load on the scale, the coaction of tooth53 with disk 33 will in all cases provide accurate load settings of thepounds and ounces orders.

If the load on the scale is a fraction greater than an even poundage,disk 30 will move counterclockwise (Fig. 3) past tooth 53 and the pointof a tooth 3| corresponding to the even pound value will be to the leftof tooth 53 by an amount equivalent'to the fractional value above theeven pound value. For example, a load of 25 pounds, 8 ounces will movethe point of a tooth 3| corresponding to 25 pounds to the left of tooth53 by half a notch width or by a distance equivalent to eight ounces.Now, movement of tooth 53 towards disk 30 causes the tooth to enter thenotch 3| which corresponds to the pound range above the last even poundpoint and to cam against the inclined side of this notch to move disk 33backwards until the tooth is fully seated in the notch. As a result ofthis cam action, disk 33 will have been set back half a tooth notchdistance or through an angle equivalent to eight ounces. The reversemovement of disk 33 is proportionally transmitted to stepped disks 33and 43 to bring their steps 4|-|I and 42-3 to control position. Further,as a result of the action of tooth 53, disk 30 is locked in an evenpound value.

The means for transmitting reverse movement of disk 33 to the ouncedisks 33 and 43 will now be described.

Control bar 44, as previously explained has a vertical slot 53 receivinga pin 5| extending from block 52 which is formed with tooth 53.Connecting bar 44 with block 52 is a spring 55 normally holding theblock in its lowest position on bar 44,: this position being determinedby engagement of pin 5| with the lower end of slot 50, as indicated inFig. 3. Bar 44 is normally held by spring 43 at its upper limit and bar44 through engagement of the lower end of its slot 53 with pin 5| ofblock 52 is normally holding the block at its upper limit position. Inthis position of block 52, the point of tooth 53 is free of and abovethe disk 30.

Further, in the upper position of bar 44, a pin 56 near its lower end isengaged with one end of a lever 51 and holding the latter at itsclockwise limit (Fig. 3). Lever 51 is pivoted on pin 53 carried by frameplate 24 and has a slot 53 engaged by a pin 63 extending from the sideof a plate or arm 62 which is pivoted at its lower end on stud 63 fixedto frame plate 24. Rigidly a clockwise direction (Figs. 3 and 4).

wise movement of shaft, 61 under the influence of.

secured to the side" of plate 62 is 'an angle plate 66 (see Figs. 2, 3,andwl). Journaled between plates 62 and 66 is shaft 61 of a small,rubbercovered, friction roller 68 which is in front of the rim of chart26.

. When control bar 44 is upper, normal, position, tooth 53" is clearOfdiSk 30 and pin 56 is engaging lever 51 to hold the latter in itsclockwise position. In iihlS'DOSltiOIl of lever 51, its

notch 59 cams against pin 66 to hold arm 62 at the arm 62 when thus setm tains'roller'68 clear of-and out of contact wit the rim of chart 26.While these parts 44, 51, 62, and 68 are thus in home positions, theload acts on chart 26 to set it without interference from roller 68.

Fast to the left end of shaft 61 of 'roller 68 (as viewed in Fig. 2) isa disk 63 having seventeen notches 10 which correspond in clockwiseorder (Figs. 3 and 4) to 0 to 16 ounces. On the right hand end of shaft61 (as seen in Fig. 2) is wound a fine clock spring 12 connected atopposite ends to shaft 61 and plate 66 to normally, thoughlightly, urgeshaft 61 and its roller 68 in The clockspring -12 is limited byengagement of a pin 13 extending from the right side of notched disk 69.on shaft 61 (see Fig. 2) with a finger .14 rigidly projecting fromthe'upper, free end of plate 6.2.

Whenpin 1.3 and finger 14 are engaged, disk 69 is in zero position.

At the left of disk 69 (as viewed in Figs. 3 and 4.) is a pawl tooth 15carried by an arm 16 pivoted to frame stud 11. A spring 18 normallyholds arm 16 and .its pawl tooth 15 free of disk 69'.

Control bar 44 is connected to a plunger 19 of a dash pct 86 adapted todampen the downward movement of bar 44 and to cause this movement to beuniform. effectively time the down stroke of the control bar. r v

After chart 26 has been set in direct response.

to a load on the-scale, the operator depresses a start key ST to closestarting contacts ST form--- ing the following circuit (see Fig. 6)

From terminal 8|, through starting contacts.

ST, through magnet 82, and normally closed cam contacts 83 to theterminal 84.

5ft Above circuit energizes magnet82 to attract taneously closesparallel contacts 82b.

armature 82 to close contacts 82a thereby shunting starting contacts ST.The circuit will now remain energized as long as cam contacts 83 areclosed.

Armature 82' as diagrammatically shown in Fig. 6 not only closescontacts 8211 but also simul- Closing of contacts82b connects solenoid48 across the and sides of the line and as a result, the solenoid isenergized. The solenoid thereupon-depresses its core '41 to rock lever.46 downwardly.

against resistance of spring 43 and to-move control bar 44 throughitsdown stroke. The downward movement of bar 44, is resilientlycommunicated to block 52 of tooth by means of spring connection 55.

Before the point of the tooth reaches the locus of the points of teeth3| of disk 30, pin 56 releases lever 51 to permit a light spring-connected at the upper end to the frame 24 and at the lower end to pin6ll-to rock' arm 62 clockwise from the position shown in Fig. 3 to thatshown in Fig. 4. A very slight amount of clockwise movement of arm 62 issuflicient to bring the periphery of roller 68 into engagement with theits counterclockwise limit and asrshown in Fig. 3,.

The dash pot also serves to of movement ofjp awl 15.

rim of chart 26. The spring 85 at the end of this clockwise movement ofarm 62 extends in radial.

line with pin 66 and pivot 63 of'arin'62 so as to exert no turning forceon arm 62 and thereby to maintain roller 68 lightly'engagedwith chart26.

With roller 68 engaged with chart 26, the lower, zero notch 10of---.disk 63 .is directly in frontof pawl tooth 15. Immediately afterengagement of roller 68 with'chart 26, the uninterrupted, continued,downward movement of bar. 44..begins to move tooth 53 into .a notch 3|of disk 36 which is rigidly fastened to chart 26.. As previouslyexplained; the movement of tooth 53' into a notch j 3i sets disk 36 backto-the even pound load posilion and locks it in the latterposition,'mean- 'whileimoving disk 36 clockwise (Figs. 3 and 4) tosubtractthe fractional pound value of the load from the load responsivesetting of disk 31L Asa result oilthe settingof disk '30. chart 26 isalso returned an amount corresponding" to the "free-- tional pound valueofthe load. The chart 26 at, the end: of this return-movement will haveits Thus, for an eight ounce-return of chart roller 68, its shaft 61,and disk 68 are rotated counterclockwise through: ariJ angle 'cove'redby eight notches]!! of disk .69. Thus, eachnotch 10 is-equivalent to anounce load value. Initially, before return movement. of chart 1'26begins and with roller 68 engaged withJthe chart, the "pawl nose 15 isin line' with the centerof the lowest,

or zero notch-10. Should chart 26 now be re-.'

turned less than half' anounce distance; the zero notch 16 will nothavemoved past pawl nose 15- and consequently when the latter ismovedtowards disk 69, it will seat in the zero notch .10 and lock. disk 69.in its zero position. Should chart 26 be returned more than half'an'ounce distance, zero notch") will pass pawl 15 and the next, oneounce notch 10 willlie in the path arranged to pass pawl 15 at thehalf-ounce load values. For example, 1% ounces above an even line withpawl 15 while 1% ounces will bring the Thus,-. the notchesiare.

'pound load will bring'the 2 ounce notch 10 in I 1 ounce notch 16 inline with pawl .15. Should the ounce value be exactly /2, then thepointof j pawl 15 will contact a pointer disk 68 and eifec-'. tivelylock the latter in its half ounc'e position. Should, however, the pointof the pawl pass the point of disk 69 and move into the notch 16 ateither side of this point, the maximum error will be plus or minusone-half an.ounce.

As indicated in Fig. 4, disk 36 and chart 26 are locked by'tooth 53 inan even pound position after an eight ounce return movement of .chart26. As a result of the return of chart 26, roller I 68 .and disk 69 havebeen rocked counterclociv.

wise through an angle spanned by eight notches 10,ther eby bringing theninth notch 18 which represents an 8 ounce value into line with pawl15.l Now tooth 53 is fully seated in a notch 3| of disk 30 and itsdownward movement is thus,ar-

rested. Control bar 44 however continues its down stroke and stretchesspring 55 between the bar and tooth 53. The first part of the downwardmovement of bar 44 after tooth 53 has beenfully seated in a notch 31engages thepin 56 with an arm 91 pivoted on frame stud 11 and rocks thearm clockwise. Through a spring 98, the clockwise movement of arm 81 isresiliently transmitted to arm 19 thus bringing pawl 15 into lockingengagement with 8 ounce notch 19. Disk 99 is now locked in adifferential position corresponding to the fractional load value.Operating under control of disk 99 are means to correspondingly setounce disks 39 and 49, as will now be explained.

Frame 29 has a stud 99 which is to the left of shaft 91 of roler 99 (asviewed in Fig. 2) When roller 99 is engaged with chart 29, stud 99 andshaft 91 are in axial alinement. Rotatably mounted on stud 99 is a gearsector 9| integrally provided opposite the gear teeth with a finger 92.Finger 92 is adapted to engage a pin 93 extending from the left side ofdisk 99 (see Fig. 2).

When roller 99 is moved into engagement with chart 29 and disk 99 isstill in zero position, pin 93 is engaged by finger 92. This is \thehome position of the finger and of its associated parts. After disk 99is moved counterclockwise to an ounce setting, then by means to bedescribed later, the finger 93 is moved in the same direction to engagepin 92 and be stopped thereby in a V position-corresponding to that ofdisk 99.

Gear sector 9| is meshed with a gear sector 94 fast to the left end of ashaft 95 which at the right end (as viewed in Fig. 2) rigidlycarries alarger gear sector 96. Gear sector 99 in turn meshes with a gear sector91 fast to. sleeve shaft 39 and ounce disks 39 and 49. Thus, as finger92 of gear sector 9i moves from its initial, home,

or zero position to engage pin 93 of disk 99, gear sectors 92, 94, 99,and 91 move through angles proportional to the ounce setting of disk 99and therefore corresponding to the fractional load value. As a result,shaft 39 and its ounce disks 39 and 49 are set with the steps 4| and 42representing the ounce values at the control position. i

Fig. 4 indicates the positions of disks 39 and 49 at the end of theirsetting according to an eightounce value. A step 4|--9 and a step 42-9are in control position.

-The movement of gear sector 9I-and therefore of the elements 9.2, 94,95, 99, 91', 39, 39,

and 49under ;control of disk 99 is governed as follows:

, Immediately after bar 49 through its pin 59 has caused the locking bypawl 19 of disk 99,

the lower end of the bar engages the upper one of a pair of springblades 99 and I99 to close switch "I, the points of which are carried bythe spring blades. Referring to Fig. 6, closing of switch I9Iestablishes the followingcircuit:

Circuit A.--From terminal 9|, through switch I.9I and clutch magnet I92to terminal94. 1

The above circuit energizes magnet I92. R.e--

ferring to Fig 5, magnet I92 when energized rocks latch lever I92acounterclockwise to release a clutch-pawl I 95.. The pawl is carrledby adisk I99 rigidly carried by ,a shaft 191 journaled between frame plates24 and25 Rotatably carried by shaft in at one side of disk I99 are therigidly conected' worm gear I99 andv ratchet disk I99. Gear I99 mesheswith worm I'I9 on shaft III of motor M. Motor M is set in-operation atthe beginning of a series of weighing and recording operations -and-maybe considered as in continuous operation. Accord- .ingly, ratchet diskI99 is continuously rotating.

1 -Now when latch I920. is released by magnet I92 from clutch pawl I95,9. spring 2 moves the 34-2 in control pawl tooth into engagement withthe teeth of ratchet] disk I99 causing the latter to impart rotation todisk I99 and its shaft I91.

Referring to Figs. 3 and 4, shaft I91 has a box cam disk I I5.formed atone side with cam groove II9. Riding in groove H9 is a follower pin 1extending from the side of a link II9 which is slotted at the left endto receive shaft I91 and pivoted at the other end to a lever II9. LeverH9 is connected by a link I29 to an arm I2l rigidly carried by a sleeveI22 rotatably mounted on shaft 95 and heldin place against movementalong shaft 95 by opposite bushings I23 pinned to the shaft (see Fig.2). Also fast to sleeve I22 is an arm I 24 extending oppositely to armI2I. Arm I24 has a stud I25 projecting into an arcuate slot I29 cut ingear 99 and is connected to gear 99 by a light spring I21.

Shaft I91 of cam disk II has been set rotating, as previously described.During the first 60 (see the timing diagram, Fig. 7) of the revolutionof disk II5, its cam groove II9 coacts with follower pin II1 to movelink 9 to the right away from the home position shown in Fig. 3.

As link 9 moves to the right, it rocks'lever ||9 clockwise and thelever, in turn, through link I29 rocks ann I2I and its sleeve shaft I22clockwise away from their initial positions shown in Fig. 3. As sleeveshaft I22 rocks clockwise its arm I24 moves in the same direction andthrough light spring I21 yieldingly draws gear 99 after it. As gear 99is fast to shaft 95, the latter is also moved clockwise. Gear 94 on theshaft thereupon rocks gear 9| on stub shaft 99 counterclockwise untilfinger 92 engages pin 93 of locked disk 99. As a result, gears 9|, 94,and 99, are stopped after being moved through angles corresponding tothe ounce setting of disk 99. Arm I24 which actuated these gears throughspring I21 into their differential positions, continues moving to theend of its forward stroke after the gears are arrested under control ofdisk 99 and spring I21 stretches.

As gear 99 rotated clockwise, it rocked meshed gear 91 and its sleeveshaft 39 counterclockwise to moveounce disks 39 and 49 in the latterdirection. Thus, if as previously assumed, disk 99 has been set in an 8ounce position, then rigidly connected disks 39 and 49 will be movedfrom their home positions shown in Fig. 3 to the .positions shown inFig. 4.

At this point, all the stepped disks are set in control positionsaccording to the even pounds and fractional pounds of load on the scale.Thus for a load of 25 lbs. 8 ounces,.disk 32 has a step position, disk33 has a step 35-5 in control position, disk 39 has its step 4I9 incontrol position, and disk 49 has its step 429 in control position.

The control positions of the several {stepped disks are the positionswhich are in line with sensing fingers I39, one for each of the disks.

The action of these fingers and the means controlled thereby is similarand therefore only one need be specifically described, the units ofounce sensing finger I39 being selected.

The forward stroke of arm I24 and the setting of ounce disks 39 and 49are completed at 99' of the revolution of shaft I91. Cam groove II9 hasan arcuate portion permitting the arm I24 to dwell at the end of itsforward stroke until 215 of the revolution of shaft I91 .(see Fig. 7).

Disk H5 is formed at the side opposite groove II9 with another separatebox cam groove I32 within which is the follower I33 of an arm I34 linkI31 to an arm I36 fast to a shaft I36- Shaft I39 rigidly carries bailarms I40 connected at their outer ends by a bail .rod I42. Rod I42 isseparately connected by 'individual springs I43 to each of four leversI44 (only one is shown) which are freely pivoted on shaft I39. Eachlever I44 is pivotally' connected at its upper end to a separate one ofthe'sensing fingers I30.

As indicated bythe timing diagram, between and of the revolution of diskH5 and while arm I24 is idling at the end of its forward stroke, camgroove I32 acts on follower I33 to rock arm I34 and its shaft I35counterclockwise from their home positions shown in Fig. 3. Arm I36 ofshaft I,35 thereby rocks counterclockwise and through link I31 rocksshaft I39 clockwise. As a result, rod I42 moves clockwise and throughsprings I43 yieldably moves levers I44 in the same direction. As leversI44 move in this direction, they bring fingers I30 .into engagement withthe control steps of the disks 32, 33, 39, and 40.

The fingers are stopped in difierential posi-- tions'c orresponding tothe heights of the steps which are in; control positions. When a fingerI30 is thus arrested in a differential position, its

operating arm I44 is likewise and similarly arrested. Rod I42 howevercontinues to the end of its clockwise stroke and stretches springs I43after the levers I44 have been arrested. Rod I42 now idles under controlof cam groove I32 at the limit of its clockwise stroke until 210 of thecycle.

Each lever I44 is formed at its lower end with :teeth I46meshed with apinion I41 of a type wheel -I48. When lever I44 is set in differentialposition, through teeth I46 it rotates pinion I41 and type wheel I48 tobring-into printing position that type lug intended for'pri'nting thedigit represented by the differential position of lever I44. Since thisdifferential position is determined by the step engaged by finger I30,it is evident that each type wheel I48 is set to print the valuecorresponding to the height of the control step. Thus, the units ounceorder type wheel I48 is set to print 8 under control of step 42-6 ofdisk 40, as shown in Fig. 4.

For'a load of 25 lbs. 8 ounces, the tens and units disks 32 and 33 willrespectively control their sensing fingers I30 and connected levers I44to'set the tens lbs. order and the units lbs. order type wheels to print2 and 5, respectively while ated tens of ounces and units of ouncesorder.

' type wheels torespectively print 0 and 8.

A t 125 (see Fig. '1) of. the revolution of shaft I01, all the typewheels I48 have been set according to the load and remain set whilerodI42 is idling-at the end of its forward stroke until 150 of the cycle.During this idling period, printing, takes place. The means 'foreffecting printing comprises a shaft I50 geared one-to-one by gearingI5I to shaft I01.- Shaft I50 has a cam I52 coacting with follower leverI53 rotatably mounted on a shaft I54. Lever I53 is connected by springI55 to a hammer I56. At of the cycle, cam I52 permits lever I53 to berocked clockwise by a spring I51.' The lug I58 on lever I53 held engagedwith hammer I56 by spring I55 thereupon imparts clockwise movement tothe hammer The drop in cam I52 is such that lever I53 stops clockwisemotion before hammer I56 strikes the type lugs-of type wheels I48. Dueto 75 its momentum, the hammer continues to move further than lever I53and strikes thetype wheels a sharp blow. Between the hammer andtypewheels is a card guide or chute I59 in which a card or sheet C isinserted before the weighing operation. Between the card,C- and typewheels is an inking ribbon R. Thus, the hammer when it strikes the typewheels causes the latter to print the load record on card 0.

After the weight record has been made, the parts are ready to berestored.

As indicatedin the timing diagram (Fig. '7), the printing operation iscompleted at about 135 of the cycle. -At of the cycle, cam groove I32functions to move rod I42 counterclockwise and the rod engages -thelevers I44 to restore them andtheir connected sensing fingers I30 andtype wheels I46 to zero on home positions. The

restoration of these parts is completed at 210 of the cycle.

The stepped disks 39 and 40 are now free to be restored. At 215 of thecycle, cam groove H6 functions to cause counterclockwise rocking of armI24 and its stud I25; As the stud moves counterclockwise; it encountersthe lower end wall of slot I26 and positively restores gear 96 and itsconnected parts 91, 38, 39, 40, 95, 94, 9|, and 92 to their homepositions. The restoration of the latter parts is completed at 275 ofthe cycle.

As shown in Fig. 5, shaft I01 has a cam I65 which is engageable with thelong blade 830 of contacts 83 to separate it from short blade 83I tothus open contacts 83. As indicated in Fig. 7, between 280 and 285 ofthe cycle, cam I65 opens contacts 83. This results in breaking thecircuit through magnet 82 which thereupon releases its armature 82 tocause contacts 82a and 82b to open. Cam I65 permits contacts 83 toreclose before the end of the cycle of shaft I01 but since contacts 62aare then open, the circuit through magnet 82 cannot be made again exceptby the closing of starting contacts ST. 1

Opening" of contacts 821) breaks the circuit through solenoid 48 andcontrol bar 44 starts its return or upward stroke. As bar 44 moves up,it releases blade 99 and switch IOI opens, thereby breaking'the circuitthrough clutch magnet I02. This occurs at, about 285 of the singlerevolution of shaft 101. With clutch magnet I02 now deenergized, springI02 returns latch mm to in itial position for intercepting the tail ofclutch pawl I 05. When disk I06 and its shaft I01 have made onerevolution, latch I020. engages pawl I05 and rocks it out of engagementwith ratchet disk revolution.

K As bar 44 is now moving up, pin 56 leaves arm 81 permitting springs 68and 18 to retract lock tooth 15 from the notch 10 of disk 69 engaged bythe tooth. During a further part of the return stroke of bar 44, pin 56engages lever 51 to rock it clockwise (Figs. 3 and 4) causing its slot59- to cam against pin 60 for rocking arm 62 counterclockwise. Thismovement of arm '62 withdraws roller 68 from engagement with the rim ofchart 26. As bar 44 moved to bring its pin 56 from arm 81 to lever 51,through spring 55 it' moved tooth 53 upwardly. Following the point ofthe return stroke at which roller 68 was disengaged from chart 26, thelower end of slot 50 of bar 44 en- A load is placed on platform I0. Theweight of the load causes levers I2, I3, and I6 to depress tape I6 tothereby rock pendulum shaft I6 clock- 10 wise (Fig. 1) through an areequivalent to the /load. Through gears and 2I, shaft I8 similarly rocksweight shaft 22 and its rigidly. carried parts, chart 26, tens ofpounds" stepped disk 32 and units of pounds stepped disk 33. 15 Theoperator now depresses start key ST (Fig. 6) to close contacts STthereby forming a circuit through magnet 82. Energization of the magnetcloses contacts 82a to shunt out the starting contacts ST and closescontacts 62b to enerbar 33 through its down stroke.

The initial part of this stroke withdraws pin 66 of bar 43 from lever61, permitting a light spring 06 to rock the arms 62 and 66 to bring 25the friction roller 68 carried by the arms from the position shown inFig. 3 to the position shown in Fig. 4 in which the roller is engagedwith the rim of chart 26. The next part of the stroke 10f bar 44 startsmoving tooth 53 into a notch 3! of disk and as the tooth moves intoth'enotch it earns the disk 30 clockwise in a direction reverse to that inwhich it is moved by the load. When I for operation according torotation of the wheel by the disk. a

the tooth is seated flush in the notch 3|, it has set disk 30 backtrough an angle corresponding to the ounces above the even pound'age andhas locked the disk In such position. As disk 30 is fast to chart 26,the latter and'its shaft 22 are correspondingly set back. Stepped disks32 and 33 are also set back and this results in the central position ofa pound step 35 of disk .33 being in front of its sensing finger I30,thus removing the danger of the finger engaging the point of the step 36and sliding on the. point to abutthe incorrect tooth. I

As chart 26 is set back, it frictionally rotates roller 66counterclockwise (Figs. 3 and 4) through anangle corresponding to theounce orders of the load. When the chart 26 has been locked in its evenpound position, disk 69 on shaft. of

x roller 30 has a notch- 10 corresponding to the ounce load in positionto be engaged by a pawl 13. The downward movement of bar 43 continuesandpin 66 strikes lever 01 to rock pawl 16 into, engagement with thenotch 10 of disk 69 which corresponds to the ounce load. At the end ofthe down stroke of bar 43, it closes switch IOI.

When switch IOI closes, clutch magnet I02 is energized to release shaftI01 for a single revolution cycle. Referring to the. timing diagram,Fig.

50 7, between 0 and of this cycle, a cam groove II6 of disk H5 on shaftI01 causes clockwise movement of an arm I24 to move parts 9|, 92;

93, 95, 96, 91, 33, 39, and 40 in accordance with the ounce setting ofdisk 69. Astep ll of disk 39 5 and a step 42 of disk 30 representing thetens and units ounce orders of the load arenow in a front of theirsensing fingers I30.

Following the setting of disks 39 and 30, a cam groove I32 of disk II6causes the levers I to be 70 differentially positioned under control ofthemgagement of sensing fingers I30 with the steps 34, 36, I, and 42 ofthe tens of pounds disk 32, units of pounds disk 33, tens of ounces disk39, and

units of ounces disk 40. The levers I, when differentially positioned.

gize solenoid 38. Solenoid 48 now moves control set the-printing wheelsI30 to printthe load" values;

At of the cycle, cam I62 causes hammer I66 to strike the type wheels formaking a load value imprint on a card C.

Following the printing operation cams 6, I32, and I52 restoretheir-associated parts to initial positions. 1 At 285 of the cycle, camI66 opens contacts 03 to cause deenergization' of solenoid 33 andmagnet. 02.. Solenoid III now rises and switch IOI- opens and breaks"thecircuit. through clutch magnet I02. Deenergization of magnet I02results in shaft I01 being stopped after it'has made one revolution. Asbar 43 moves through its return stroke, the parts directly controlledthereby .return to initial positions. a

While only a'single embodiment of the inventicn has been disclosed, itistobe understood that any variations, departures, or modificationsderived from the principles of theinvention are to be considered aswithin the bounds of the invention which is to be limited only by thescope of the claims.

I claim: 1. In a load weighing scale; the combination of a rotatabledisk primarily settable in a load the load position in proportion to afractional value of the load, a friction-wheel .frictionally rotated byengagement with the diskv during roposition, means for rotatingsaid'disk away from a tation of. the disk by said means, and indicatingmechanism controlled by the friction, wheel 2. In a load weighing scale;the combination of 'a rotatable disk primarily settablein --a loadpositiornmeans for eflfecting a secondary setting of the disk torotateit in proportion to -a frac-' tional value of the load, a frictionwheel engage-n able with the rim oi; the disk to be frictio'nallyrotated .thereby during its secondary setting, and

indicating mechanism'controlied by said friction wheel for'operationaccording to -'said fractional load value.

3. In a load weighing scale; the combination of a rotatable diskprimarily settable in a position corresponding to the load, means .toeffect a secondarysetting-of the disk to rotat'eit away from said loadposition in proportion to a fractional value of the load, a frictionwheel normally free of the disk, means controlled by operation of thefirst-mentioned means preliminary to effecting said secondary settingoperation for engaging said wheel with said disk to thereby cause thedisk to frictionally rotate the wheehduring the secondary settingoperation in accordance with-said frac tional load value, and indicatingmechanism controlled by said wheel according to its rotation.

a. In a load weighing scale the combination of a rotatablyv mounted diskresponsive to the force of the load to be set thereby in load posi'tion, means operable subsequently to load setting of the disk foreffecting a secondary setting of the disk by rotating-it away from theload position in proportion to. a fractional load value. a.

friction wheel of lesser diameter than the disk,

normally free of the disk and movable into engagement with the disk tobefrictionally rotated by the latter during its secondary settingthrough a greater angle than the angle of secondary rotation of thedisk, movement multiplying mechanism controlled by the wheel Inaccordance with rotation of the latter to further multiply the secondarymovement of the disk. and mamas: de-

vices controlled by said mechanism for operation in proportion to saidfractional load value.

5. In a load weighing scale; the combination of a member movableproportionally to the load to a position corresponding to whole andfraciional values of the load, means to effect a supplementary movementof the member in proportion to the fractional load value, a plurality ofelements, one having steps representing the digital values of a lowerdenominational order of the fractional load value, the other havingsteps representing the digital values of a higher order of thefractional load value, means controlled by the member in accordance withits secondary movement for commonly actuating said elements to selectsteps of each representative of the different orders of digitsrepresenting the fractional load value, fingers for sensing the heightsof the selected steps, and multi-denominational order indicating devicescontrolled by the fingers to indicate the fractional load value in itsseveral orders.

6. In a weighing scale; the combination of a notched member movableproportionally to the load, a tooth movable into a notch of said memberand arranged and constructed to cammingly coact with a wall of saidnotch during movement into the notch to effect a supplementary movementof the member proportional to a fractional load value, and indicatingmechanism controlled by the member according to its supplementarymovement to indicate said fractional load value.

'7. In a weighing scale; the combination of a rotatable disk movableproportionally to the load and having notches with inclined sides, thewidth of each notch corresponding to a single preselected unit value ofthe load, a knife edge shaped to fit into a notch of the disk, means formoving the knife edge into a disk notch to cause the knife edge to camagainst the inclined side of the notch and rotate the disk in proportionto a fraction of such unit value, an indicating device, and mechanismcontrolled by the disk for operating the indicating device in accordancewith the extent of rotation of the disk by said knife edge to therebyenter said fractional value of the load unit into the indicating device.

8. The combination as defined in claim '7, the mechanism controlled bythe disk including a wheel normally free of the disk, and moved intoengagement with the disk under control of aforesaid knife edge operatingmeans, said wheel after engagement with the disk being rotated therebyreversely to rotation of the disk and in proportion to the fractionalunit movement of the disk, and means cooperating with the wheel toconvert rotation of the latter into equivalent operation of theindicating device.

9'. The combination as defined in claim 7, aforesaid mechanism includinga cyclically operable actuator, a device controlled by the knife edgeoperating means for setting said actuator in operation for a singlecycle, and means controlled by the actuator for operating saidindicating device under control of said disk.

10. In a load weighing scale; a rotatable disk primarily settable in aload position, means for effecting a secondary movement of the disk byrotating it away from the load position in proportion to a fractionalvalue of the load, a wheel of lesser diameter than the disk havingperipheral engagement with the disk and rotated by engagement with thedisk through a greater angle than the latter during the secondarymovement of the latter, and indicating mechanism controlled by the wheelfor operation according to the rotation of the wheel by the disk.

11. In a load weighing scale; a rotatable member primarily settable inaload position, means for effecting a secondary movement of the memberby rotating it away from the load position in proportion to a fractionalvalue of the load, a rotatable device of lesser radius than the memberand having peripheral engagement therewith to be rotated thereby duringsecondary movement of the member through a greater angle than thelatter, and indicating mechanism controlled by the device for operationaccording to the rotation of the device by the member.

FREDERICK Q. RAST.

